EP2047156B1 - Dispositif de soupape à système de commande auxiliaire manuel - Google Patents

Dispositif de soupape à système de commande auxiliaire manuel Download PDF

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Publication number
EP2047156B1
EP2047156B1 EP07725785A EP07725785A EP2047156B1 EP 2047156 B1 EP2047156 B1 EP 2047156B1 EP 07725785 A EP07725785 A EP 07725785A EP 07725785 A EP07725785 A EP 07725785A EP 2047156 B1 EP2047156 B1 EP 2047156B1
Authority
EP
European Patent Office
Prior art keywords
actuating
section
valve
unit according
valve unit
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP07725785A
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German (de)
English (en)
Other versions
EP2047156A1 (fr
Inventor
Jürgen Lieb
Eberhard Wolter
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Festo SE and Co KG
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Festo SE and Co KG
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Publication date
Application filed by Festo SE and Co KG filed Critical Festo SE and Co KG
Publication of EP2047156A1 publication Critical patent/EP2047156A1/fr
Application granted granted Critical
Publication of EP2047156B1 publication Critical patent/EP2047156B1/fr
Not-in-force legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/0624—Lift valves
    • F16K31/0627—Lift valves with movable valve member positioned between seats
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/44—Mechanical actuating means
    • F16K31/52—Mechanical actuating means with crank, eccentric, or cam
    • F16K31/524—Mechanical actuating means with crank, eccentric, or cam with a cam
    • F16K31/52408—Mechanical actuating means with crank, eccentric, or cam with a cam comprising a lift valve
    • F16K31/52416—Mechanical actuating means with crank, eccentric, or cam with a cam comprising a lift valve comprising a multiple-way lift valve

Definitions

  • the invention relates to a valve device, comprising at least one electrically actuated valve which has a valve member movable by electrical actuation between a first switching position and a second switching position, which is associated with a manual override device having an axially displaceable actuating tappet, which counteracts by manual application of an actuating portion the force of a return spring from an unactuated position is displaced into an actuated position to act with a drive portion on the valve member and to shift it from the first switching position to the second switching position, and which is releasably lockable by locking means in the actuated position to the To keep valve member by constant action in the second switching position.
  • One from the DE 43 09 695 A1 known valve device of this type includes two trained as pilot valves electrically actuated valves, which are each equipped with a manual override.
  • the manual override device allows independent of the electrical control, purely manual switching of the valve member of the electrically actuated valve from a voltage applied to a valve seat first switching position in a lifted from the valve seat second switching position.
  • the Adjusting force applied by means of a sliding actuating plunger which is biased by a return spring in an unactuated position.
  • the actuating tappet has a hand-operable actuating portion and an opposite, acting on the valve member drive portion.
  • the actuating plunger is a one-piece, rigid component.
  • the actuating plunger can be releasably locked in the actuated position.
  • a rotatable locking element can be pivoted over the actuating portion of the actuating plunger.
  • the actuating portion and the drive portion of the actuating plunger are formed as in the direction of displacement of the actuating plunger relative to each other displaceable parts, between which they press away from each other, in comparison to the return spring strength tolerance compensation spring is effective, the manually actuation force exerted on the actuating portion can transmit to the drive portion, wherein the return spring engages the drive portion and wherein the locking means associated with the actuating portion and are formed so that the tolerance compensating spring is always taut at locked in the actuated position of the actuating plunger actuating portion than in the unactuated Position of the actuating tappet.
  • tolerance compensation spring is strong enough to transmit the manually applied to the operating portion actuating forces on the drive section, so that initially both sections and thus the entire actuating plunger can move, such as if it were a uniform component.
  • the tolerance compensation spring is particularly strong enough to transmit the required to switch the valve member in the second switching position force. If the valve member is switched to this second switching position and blocked by abutment with a stop on a further movement, the tolerance compensation spring allows a further relative movement of the actuating portion with respect to the drive portion until the locking operation has been performed. For the return to the unactuated position, the restoring spring which is independent of the tolerance compensating spring and which acts only on the drive section is responsible.
  • the tolerance compensation spring so on the one hand, the driving coupling between the actuating portion and the drive section accomplished, but on the other hand also a compensation of tolerances causing relative movement between the operating section and drive section allowed.
  • the tolerance compensating spring is more tensioned when locked operating portion than unconfirmed actuating tappet, it is ensured that the drive section always acts on the valve member with a second switching position ensuring the actuating force.
  • the tolerance compensating spring can be further displaced by the actuating section continue to be compressed until the lock is possible.
  • the valve device is in particular designed so that the valve member rests in the first switching position with simultaneous closure of a valve channel to a valve seat and is lifted in the second switching position against a spring force of the valve seat to release the valve channel.
  • the electrically actuatable valve is preferably a solenoid valve with a solenoid device for the electrically induced actuation of the valve member.
  • the principle according to the invention can also be transferred to other types of valves.
  • the operating portion and the drive portion may in principle, despite their relative displaceability be common components of a one-piece component, if a relative mobility ensuring yielding connection is present, for example, a connection area in the manner of a bellows.
  • a relative mobility ensuring yielding connection is present, for example, a connection area in the manner of a bellows.
  • preferred is a design in which the actuating portion and the drive portion are formed as two separate parts. So that the actuating tappet nevertheless forms a tappet unit, these two separate parts can be inserted into one another transversely to the direction of displacement of the actuating tappet.
  • the actuating portion and drive portion in the direction of displacement of the actuating plunger relative to each other slidably with each other in Engage.
  • the mutual engagement is a mutual stabilization in the relative movement, so that a secure guidance is ensured, even without extensive management measures are taken on the other valve components.
  • the tolerance compensating spring can be designed to be under constant preload and to urge the two portions in opposite directions even when the actuating plunger is unactuated.
  • the tolerance compensating spring in the unactuated position of the actuating plunger still undergoes no bias and is compressed in connection with the locking process.
  • stop means can be dispensed with, which prevent the two sections from moving apart.
  • the tolerance compensation spring can be accommodated in the interior of the actuating tappet.
  • the plunger system is designed so that the existing between the actuating portion and the drive portion axial displacement clearance is so large that between these two sections in principle, a further mutual approach permitting residual margin remains when the operating portion is locked.
  • a comprehensive tolerance compensation is particularly reliable possible, including compensation of occurring due to temperature fluctuations material expansions.
  • a locking latch would be possible, wherein the locking takes place automatically when the operating portion has been moved by a certain distance.
  • a higher level of security against accidental switching back to the unactuated position is regularly mediated by such locking means, for the activation of which a further handling measure is required in addition to the axial displacement of the actuating portion.
  • the locking means may in particular be designed so that they can be brought into and out of locking engagement by turning the actuating portion about its longitudinal axis.
  • the actuating portion may in this case form a rotary latch member.
  • the valve device is designed in particular as a pilot-operated multiway valve.
  • it contains a fluid-actuated main valve on which the electrically actuated valve equipped with the manual override device is arranged as a pilot control valve.
  • FIGS. 1 . 3 and 6 each show in longitudinal section an end portion of a generally designated by reference numeral 1 valve means which is formed here in the form of a pilot-operated multi-way valve. It contains an in FIG. 1 dash-dotted lines indicated main valve 2 per se known type, which has a main valve housing 3, in which a switchable between different switching positions main valve member 4 is arranged. Depending on the switching position, the main valve member 4 can not connect main valve channels (not shown) in different patterns with each other in order to allow or prevent certain fluid flows.
  • a supply channel which can be connected to a pressure source, a discharge channel which can be connected to a pressure sink, for example the atmosphere, and at least one working channel which can be connected to a consumer to be actuated.
  • the working channel can then be connected depending on the switching position of the main valve member 4 either with the feed channel or with the discharge channel.
  • an electrically actuated pilot valve 5 is arranged in each case. In the drawing, only one of these two pilot valves 5 is shown, the other is designed in the same way.
  • the two pilot valves 5 can control the fluid loading of the main valve member 4 to shift this in the respectively desired switching position.
  • On the second pilot valve can be omitted if, for example, a spring means for returning the main valve member 4 is used instead.
  • pilot valves 5 can also be connected together to one and the same end region of the main valve 2 be arranged, in particular on the model of DE 43 09 695 A1 ,
  • the pilot valve 5 includes a one- or multi-part main body 6, which is attached to the front side of the main valve housing 3.
  • An electric drive device in the form of a solenoid device 7 is attached to it, in particular on the front side.
  • the pilot valve 5 of the exemplary embodiment is therefore a solenoid valve.
  • the invention can also be implemented in other types of valves, for example in piezo valves.
  • the electromagnet device 7 can be electrically controlled such that it is a valve member 8 under execution of a linear switching movement 12 between a FIG. 1 apparent first switch position and one off Figures 3 and 6 displaced apparent second switching position.
  • the valve member 8 is for this purpose an integral part of a movable armature 13 of the electromagnet device 7, which is adjustable by electrically energizing a coil device 14.
  • the required electrical actuation signals can be fed via an electrical interface device 15.
  • valve member 8 and the movable armature 13 may also be designed as separate parts, which are drivingly connected to one another in any desired manner.
  • the valve member 8 is in particular formed plunger-like and has at its two end faces via a first and second sealing surface 16, 17.
  • the first sealing surface 16 is located opposite a first valve seat 18, which framed the mouth of a running in the base body 6 first valve channel 22.
  • the opposite second sealing surface 17 is located opposite a second valve seat 19, which is preferably formed on the electromagnet device 7 and which surrounds the channel mouth of a second valve channel 23, which opens out to the atmosphere at the other end.
  • the first valve channel 22 is in operation of the valve device 1 with a pressure source in connection, wherein he over the in FIG. 1 dash-dotted lines indicated channel profile may be connected to the above-mentioned feed channel of the main valve 2.
  • the pressure source supplies pressurized fluid under atmospheric pressure, in particular compressed air.
  • the first valve seat 18 is located in a formed in the base body 6 valve chamber 25, which communicates via a third valve channel 24 in constant communication with an associated with the main valve 2 Beaufschlagungshunt 26 which is bounded by a drivingly connected to the main valve member 4 Beaufschlagungs constitutional 27.
  • valve member 8 If the valve member 8 is in the first switching position, it disconnects the first valve channel 22 from the valve chamber 25 and at the same time connects the third valve channel 24 with the second valve channel 23 leading to the atmosphere.
  • the loading chamber 26 is consequently depressurized, so that the main valve member 4 has a out FIG. 1 can assume apparent switching position in which the loading chamber 26 has a minimum volume.
  • valve member 8 In the second switching position according to Figures 3 and 6 the valve member 8 is lifted from the first valve seat 18 and abuts with its second sealing surface 17 on the second valve seat 19. As a result, the second valve channel 23 is shut off and it can pressure medium from the open first valve channel 22 via the valve chamber 25 flow into the Beaufschlagungshunt 26 to apply the main valve member 4 and to shift to another switching position.
  • the two sealing surfaces 16, 17 are expediently components of separate or a common rubber-elastic sealing element 28, which belongs to the valve member 8.
  • the pilot valve 5 is additionally equipped with a manual override 33, which makes it possible to move the valve member 8 without the involvement of the solenoid device 7 by a purely manually applied actuation force from the first switching position to the second switching position and there to hold as long as desired.
  • the manual override device 33 is used primarily for maintenance purposes or during a test operation of the valve device 1.
  • the manual override device 33 includes an actuating plunger 34, which is arranged to be linearly displaceable in the direction of its longitudinal axis 36 in a guide recess 35 of the base body 6 which is open toward the outer surface of the main body 6.
  • the actuating plunger 34 is in particular arranged so that its longitudinal axis 36 and consequently the displacement direction 46 transversely and preferably at right angles to the direction of the switching movement 12 of the valve member 8 extends.
  • the actuating tappet 34 is subdivided into two axially successive longitudinal sections, a drive section 44 arranged in the region of the inner end section 37 and an actuating section 43 located in the region of the opposite outer end section 45 of the guide recess 35. Since the outer end section 45 leads to the outer surface of the main body 6 the actuating portion 43 located there accessible from the outside, to be acted upon manually with an actuating force F B , which acts in the direction of the inner end portion 37.
  • the actuating portion 43 and the drive portion 44 are decoupled from each other so that they are within certain limits in the direction indicated by a double arrow axial displacement direction 46 of the actuating plunger 34 relative to each other.
  • the available for this relative movement axial displacement clearance is indicated in the drawing at "S".
  • Actuating portion 43 and drive portion 44 are suitably formed as separate parts, as well as from FIG. 5 is apparent. If the required displacement margin is maintained, however, the two sections 43, 44 may also be connected to each other, in particular by a rubber-elastic connecting portion (not shown).
  • a spring is effective, which is referred to as a tolerance compensation spring 47 due to their respective function. It is arranged so that it pushes the two sections 43, 44 axially from each other.
  • a compression spring in particular as a helical compression spring, being housed for realizing compact dimensions, in particular in the interior of the actuating tappet 34. This is clearly visible from the sectional views.
  • the tolerance compensating spring 47 is arranged coaxially with the two sections 43, 44 of the actuating plunger 34.
  • the tolerance compensating spring 47 By the tolerance compensating spring 47, the two sections 43, 44 are biased in the spaced-apart relative position. In other words, the tolerance compensating spring 47 already has at least a slight pretension when the two sections 43, 44 assume the disengaged relative position.
  • the latter is predetermined by stop means 48, which prevents a further moving apart of the two sections 43, 44.
  • stop means 48 is expediently also the pushing together of the two sections 43, 44 limited, so that they ultimately pretend the already mentioned displacement margin "S".
  • the stop means 48 consist of transverse to the direction of displacement 46 engaging behind stop projections 52, 53 at the two sections 43, 44.
  • these stop projections 52, 53 in pairs and At the same time define two holding portions 54, 55, with which the two sections 43, 44 of the actuating plunger 34 are inserted into one another transversely to the longitudinal axis 36 during its assembly.
  • the two holding portions 54, 55 expediently also a rotation between the actuating portion 43 and the drive portion 44 is caused.
  • a return spring 56 of the actuating plunger 34 is axially outwardly in the direction of FIGS. 1 and 2 apparent unconfirmed position.
  • the actuating plunger 34 against the force of the return spring 56 from the unactuated position in the Figures 3 and 4 be moved apparent actuated position. If a locking measure that is still to be explained is dispensed with and the actuating force F B is subsequently removed again, the return spring 56 presses the actuating tappet 34 back into the unactuated position.
  • the return spring 56 engages on the part of the actuating plunger 34 exclusively on the drive section 44. It acts between this drive section 44 and the base body 6, wherein it is expediently accommodated in the inner end section 37 of the guide recess 35, ie in the region of the actuating section 43 facing away from the end face of the drive section 44.
  • the return spring can dip into a centering recess 57 of the drive section 44 .
  • the return spring 56 is preferably a compression spring, in particular a helical compression spring.
  • the tolerance compensating spring 47 is stronger than the return spring 56 and has compared to this a steeper spring characteristic. Therefore, if the actuation force F B is applied starting from the unactuated position, the actuation section 43, the tolerance compensating spring 47 and the drive section 44 initially behave like a rigid body, which as a whole is displaced axially into the interior of the guide recess 35 without relative movement of its components Compression of the weaker return spring 56.
  • the tolerance compensating spring 47 acts as a force transmission element for transmitting the force exerted on the operating portion 43 actuating force F B on the drive portion 44.
  • the displacement margin "S" remains constant at its maximum dimension.
  • the drive section 44 When displaced to the actuated position, the drive section 44, after covering a short distance across the passage 38, urges the front end portion 42 of the valve member 8. This is beveled at the forward end portion 42, as well as the drive portion 44 at its forward end. By this action, the valve member 8 is moved to the second switching position.
  • a design of the tolerance compensation spring 47 is such that it is stronger in any case is as the restoring force of the return spring 56 and plus the particular caused by the spring means 32 counterforce of the valve member. 8
  • the tolerance compensating spring 47 is dimensioned such that it can overcome this fluidic opposing force.
  • a fluid outlet to the atmosphere through the guide recess 35 is prevented, moreover, by the fact that a sealing ring 58 cooperating with the wall of the guide recess 45 is arranged on the actuating section 43.
  • the actuating plunger 34 can be releasably locked in its actuated position, so that it can not return to the unactuated position when removing the manually applied operating force F B.
  • the locking causes the actuating plunger 34 remains in its actuated position and holds the valve member 8 by constant action in the second switching position and in this case in particular presses firmly against the acting as a stop second valve seat 19.
  • locking means 62 are associated with the actuating portion 43 of the actuating plunger 34 and do not cooperate with the drive portion 44.
  • the locking means 62 suitably include a in the region of the drive portion 44 radially into the guide recess 35 projecting, firmly connected to the base 6 locking projection 63.
  • This is exemplified by a pin-like locking element 64 which is inserted into the base body 6 such that it is the guide recess 35 transversely interspersed in the region of its outer circumference according to the course of a secant.
  • the pin-like locking element 64 may be pressed into corresponding holes of the base body 6.
  • the boundary surface closer to the drive section 44 is referred to below as the inner boundary surface 67, the opposite boundary surface 68 as the outer boundary surface.
  • the outer boundary surface 67 passes directly into the outer groove flank 73.
  • the locking projection 63 and the locking groove 68 can be brought by locking the operating portion 43 about its longitudinal axis 46 in and out of locking engagement.
  • the operating portion 43 forms a rotary latch member.
  • the actuating portion 43 In order to allow a displacement between the unactuated and the actuated position, the actuating portion 43 is rotated in a release position in which the locking projection 63 comes to rest in the recess 65.
  • the two boundary surfaces 66, 67 limit the axial displacement of the actuating portion 43 in both axial directions.
  • the actuating portion 43 As long as no actuating force F B is applied, the actuating portion 43 is supported with its inner boundary surface 66 according to FIGS. 1 and 2 on the locking projection 63 from axially outward.
  • the contact pressure results here from the spring force of the return spring 56, wherein the power flow from the return spring 56 via the drive portion 44 and the tolerance compensation spring 47 to the actuating portion 43 takes place.
  • the manual override device 33 is designed taking into account the permitted manufacturing tolerances so that the valve member 8 reaches its second switching position in any case, before the outer boundary surface 67 runs onto the locking projection 63.
  • the uniform displacement of the operating portion 43, the tolerance compensating spring 47 and the drive portion 44 is stopped when the acted upon by the drive portion 44 valve member 8 due to the reaching of the second valve seat 19 can not retreat any further.
  • This intermediate state is shortly before reaching the in Figures 3 and 4 shown operating state before. In this operating state, the operating portion 43 can not be pivoted from the release position to a locking position, because the locking groove 68 is not yet at the same level with the locking projection 63.
  • the design is in particular made so that when the operating portion 43 is locked between the operating portion 43 and the drive portion 44 remains a residual margin, which in principle allows a further mutual approach of the two sections 43, 44 of the actuating plunger 34.
  • the system will be interpreted in particular so that the locking operation can only be performed if previously the operating portion 43 has been moved in a maximum displacement tolerances of drive section 44 and valve member 8 taken into account.
  • the tolerance compensating spring 47 is subject to a strong bias voltage than in the unactuated position of the actuating plunger 34. This ensures that the drive section 44 is always biased against the valve member 8 with a locking force resulting from the tolerance compensating spring 47 when the actuating tappet 34 is locked.
  • the measured in the direction of displacement 46 of the actuating plunger 34 width of the locking groove 64 is greater than the measured width in the same direction of the locking projection 63.
  • the corresponding dimensions of the locking projection 63 amount to 1.5 mm and those of the locking groove 64 to 1.7 mm.
  • the functionality of the locking means 62 can be ensured with only one recess 65 and only one locking groove 68. However, so that the locking and unlocking function can be ensured in any direction of rotation, the above-mentioned components in the embodiment in each case two times, at diametrically opposite circumferential portions of the actuating portion 43rd
  • the recess 65 merges with the respective subsequent locking groove 68 with an inclined surface 76 in order to facilitate the rotational movement.
  • the drive portion 44 is applied within the manufacturing tolerances of the valve device 1 in the locking position of the operating portion 43 at no time of this directly, but always only on the tolerance compensating spring 47. This ensures that the drive section 44 is never too strong or too low Operating force experiences, causing problems could result in the handling of the manual override 33.
  • the actuation section 43 on the end remote from the drive section 44 expediently has a tool engagement part 75 into which a screwdriver can intervene.
  • a screwdriver or an alternative tool and the operating force F B can be introduced from the human hand in the operating portion 43.
  • the measures of the manual override 33 are not limited to a pilot valve 5. Also serving for direct fluid control and not for precontrol of a main valve electrically actuated valve can be equipped with it.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetically Actuated Valves (AREA)
  • Catching Or Destruction (AREA)
  • Mechanically-Actuated Valves (AREA)

Claims (17)

  1. Dispositif à vannes, comportant au moins une vanne (5) actionnable électriquement, qui comporte un élément fonctionnel (8), qui est apte à être déplacé par une commande électrique entre une première position de commande et une deuxième position de commande et auquel est associé un dispositif de commande auxiliaire manuel (33), qui comporte un poussoir de commande (34) mobile axialement, lequel, sous l'effet d'une sollicitation manuelle d'une section de commande (43), peut être déplacé à l'encontre de la force d'un ressort de rappel (56) hors d'une position inactive dans une position active, afin d'agir par une section d'actionnement (44) sur l'élément fonctionnel (8) et déplacer ce dernier hors de la première position de commande dans la deuxième position de commande, et lequel peut être verrouillé de manière non permanente dans la position active par des moyens de verrouillage (62), afin de maintenir l'élément fonctionnel (8) dans la deuxième position de commande sous l'effet d'une sollicitation permanente, caractérisé en ce que la section de commande (43) et la section d'actionnement (44) sont réalisées sous forme de parties mobiles l'une par rapport à l'autre dans la direction de déplacement (46) du poussoir de commande (34), entre lesquelles agit un ressort de compensation de tolérances (47) pour les écarter l'une de l'autre, lequel est plus puissant que le ressort de rappel (56) et lequel peut transmettre sur la section d'actionnement (44) la force de commande exercée manuellement sur la section de commande (43), le ressort de rappel (56) entrant en contact avec la section d'actionnement (44) et les moyens de verrouillage (62) étant associés à la section de commande (43) et étant réalisés de telle sorte que, dans le cas d'une section de commande (43) verrouillée dans la position active du poussoir de commande (34), le ressort de compensation de tolérances (47) est toujours plus fortement tendu que dans la position inactive du poussoir de commande (34).
  2. Dispositif à vannes selon la revendication 1, caractérisé en ce que l'élément fonctionnel (8), dans la première position de commande, est en appui contre un siège de vanne (18) et, dans la deuxième position de commande, est soulevé du siège de vanne (18) dans le sens opposé à une force de ressort.
  3. Dispositif à vannes selon la revendication 1 ou 2, caractérisé en ce que la vanne (5) actionnable électriquement est une vanne magnétique avec un dispositif à électroaimant (7).
  4. Dispositif à vannes selon l'une des revendications 1 à 3, caractérisé en ce que le poussoir de commande (34) peut être déplacé transversalement à la direction de déplacement de l'élément fonctionnel (8).
  5. Dispositif à vannes selon l'une des revendications 1 à 4, caractérisé en ce que la section de commande (43) et la section d'actionnement (44) sont réalisées sous forme de deux parties séparées, et en ce qu'avantageusement ladite section de commande (43) et ladite section d'actionnement (44) sont enfichées l'une dans l'autre transversalement à la direction de déplacement (46) du poussoir de commande (34).
  6. Dispositif à vannes selon l'une des revendications 1 à 5, caractérisé en ce que la section de commande (43) et la section d'actionnement (44) sont en prise l'une avec l'autre de manière mobile l'un par rapport à l'autre dans la direction de déplacement (46) du poussoir de commande (34).
  7. Dispositif à vannes selon l'une des revendications 1 à 6, caractérisé en ce que sur la section de commande (43) et sur la section d'actionnement (44) sont prévus des moyens de butée (48) coopérant entre eux, qui délimitent la mobilité en sens opposés, des deux sections (43, 44) tant pour s'écarter l'une de l'autre que pour se rapprocher l'une de l'autre et, de ce fait, définissent une course de déplacement axiale maximale entre la section de commande (43) et la section d'actionnement (44).
  8. Dispositif à vannes selon l'une des revendications 1 à 7, caractérisé en ce que le ressort de compensation de tolérances (47) est mis en précontrainte axiale déjà dans la position inactive du poussoir de commande (34) et, de ce fait, maintient la section de commande (43) et la section d'actionnement (44) dans une position relative avec un écartement maximal l'une par rapport à l'autre, définie par les moyens de butée (48).
  9. Dispositif à vannes selon l'une des revendications 1 à 8, caractérisé en ce que le ressort de compensation de tolérances (47) est logé à l'intérieur du poussoir de commande (34).
  10. Dispositif à vannes selon l'une des revendications 1 à 9, caractérisé en ce que le ressort de rappel (56) est disposé dans la zone de la face frontale de la section d'actionnement (44), détournée de la section de commande (43).
  11. Dispositif à vannes selon l'une des revendications 1 à 10, caractérisé en ce que le jeu axial entre la section de commande (43) et la section d'actionnement (44) est choisi avec une dimension telle qu'il subsiste un jeu résiduel permettant en principe un autre rapprochement l'une vers l'autre de la section de commande (43) et de la section d'actionnement (44), lorsque l'élément fonctionnel (8) est déplacé par la section d'actionnement (44) dans la deuxième position de commande et que la section de commande (43) est verrouillée.
  12. Dispositif à vannes selon l'une des revendications 1 à 11, caractérisé en ce que les moyens de verrouillage (62) sont réalisés de telle sorte que le processus de verrouillage ne peut être exécuté que lorsque la section de commande (43) a été déplacée d'une valeur tenant compte des tolérances de déplacement maximum de la section d'actionnement (44) et de l'élément fonctionnel (8).
  13. Dispositif à vannes selon l'une des revendications 1 à 12, caractérisé en ce que les moyens de verrouillage (62) sont réalisés de telle sorte qu'ils peuvent être amenés en prise et hors de prise de verrouillage sous l'effet d'une rotation de la section de commande (43) autour de son axe longitudinal, et en ce que, de manière avantageuse, ladite section de commande (43) forme un organe de verrouillage rotatif.
  14. Dispositif à vannes selon la revendication 13, caractérisé en ce que le poussoir de commande (34) peut être déplacé par rapport à un corps de base (6) pour le déplacement entre la position inactive et la position active, les moyens de verrouillage (62) comportant une saillie de verrouillage (63), disposée de manière fixe sur le corps de base (6) et pénétrant à l'état non verrouillé dans un évidement (65) sur le pourtour de la section de commande (43), les surfaces de délimitation (66, 67) axiales de l'évidement (65) étant aptes à délimiter la trajectoire de déplacement de la section de commande (43) par coopération avec la saillie de verrouillage (63), une rainure de verrouillage (64), dont les dimensions, dans la direction de déplacement (46) du poussoir de commande (34), sont plus petites que celles de l'évidement (65), étant située dans le prolongement de cet évidement (65) dans la direction circonférentielle de la section de commande (43), la saillie de verrouillage (63) s'engageant dans ladite rainure de verrouillage pour le verrouillage de la position active, si l'on fait tourner la section de commande (43) lorsque la rainure de verrouillage (64) est disposée à la même hauteur axiale que la saillie de verrouillage (63).
  15. Dispositif à vannes selon la revendication 14, caractérisé en ce que la largeur de la rainure de verrouillage (64), mesurée dans la direction de déplacement (46) du poussoir de commande (34), est supérieure à la largeur de la saillie de verrouillage (63).
  16. Dispositif à vannes selon la revendication 14 ou 15, caractérisé en ce que le poussoir de commande (34) est logé de manière mobile dans le sens axial dans un évidement de guidage (35) d'un corps de base (6), la saillie de verrouillage (63) étant formée par un élément de verrouillage (64) en forme de tige qui, en suivant le tracé d'une sécante, traverse transversalement l'évidement de guidage (35) dans la zone de son pourtour extérieur.
  17. Dispositif à vannes selon l'une des revendications 1 à 16, caractérisé par une vanne principale (2) actionnable par un fluide, sur laquelle est disposée au moins une vanne (5) faisant fonction de vanne pilote, actionnable électriquement et munie d'un dispositif de commande auxiliaire manuel (33).
EP07725785A 2007-06-02 2007-06-02 Dispositif de soupape à système de commande auxiliaire manuel Not-in-force EP2047156B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2007/004907 WO2008148403A1 (fr) 2007-06-02 2007-06-02 Dispositif de soupape à système de commande auxiliaire manuel

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EP2047156A1 EP2047156A1 (fr) 2009-04-15
EP2047156B1 true EP2047156B1 (fr) 2009-12-02

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EP07725785A Not-in-force EP2047156B1 (fr) 2007-06-02 2007-06-02 Dispositif de soupape à système de commande auxiliaire manuel

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EP (1) EP2047156B1 (fr)
CN (1) CN101680566B (fr)
AT (1) ATE450738T1 (fr)
DE (1) DE502007002216D1 (fr)
WO (1) WO2008148403A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016128007A1 (fr) * 2015-02-14 2016-08-18 Festo Ag & Co. Kg Dispositif de soupape

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8210494B2 (en) * 2009-10-21 2012-07-03 Automatic Switch Company Method and apparatus for manually opening a valve with a tolerance compensating stem
EP2479465B1 (fr) * 2011-01-12 2013-04-17 FESTO AG & Co. KG Dispositif de soupape doté d'un dispositif d'actionnement auxiliaire manuel
DE102015001539B4 (de) * 2015-02-06 2022-03-17 Festo Se & Co. Kg Ventilbatterie

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3134756A1 (de) * 1981-09-02 1983-03-17 Nass Magnet Gmbh, 3000 Hannover Handbetaetigungseinrichtung fuer elektromagnetisch betaetigbare wegeventile
DE4309695A1 (de) * 1993-03-25 1994-09-29 Festo Kg Steuereinrichtung für ein Mehrwegeventil
DE10355627A1 (de) * 2003-11-28 2005-06-23 Nass Magnet Gmbh Magnetventil
DE202004004861U1 (de) * 2004-03-25 2004-06-09 Bosch Rexroth Ag Handhilfsbetätigbares pneumatisches Mehrwegeventil

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016128007A1 (fr) * 2015-02-14 2016-08-18 Festo Ag & Co. Kg Dispositif de soupape
CN107208824A (zh) * 2015-02-14 2017-09-26 费斯托股份有限两合公司 阀装置
CN107208824B (zh) * 2015-02-14 2019-07-30 费斯托股份有限两合公司 阀装置

Also Published As

Publication number Publication date
EP2047156A1 (fr) 2009-04-15
ATE450738T1 (de) 2009-12-15
WO2008148403A1 (fr) 2008-12-11
DE502007002216D1 (de) 2010-01-14
CN101680566A (zh) 2010-03-24
CN101680566B (zh) 2012-03-21

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